CN103362771B - There is the reciprocating plunger pump of the sliding bearing that stream flows through - Google Patents
There is the reciprocating plunger pump of the sliding bearing that stream flows through Download PDFInfo
- Publication number
- CN103362771B CN103362771B CN201310113844.2A CN201310113844A CN103362771B CN 103362771 B CN103362771 B CN 103362771B CN 201310113844 A CN201310113844 A CN 201310113844A CN 103362771 B CN103362771 B CN 103362771B
- Authority
- CN
- China
- Prior art keywords
- plunger pump
- transverse holes
- reciprocating plunger
- plunger
- cylinder body
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
- 239000007788 liquid Substances 0.000 claims abstract description 41
- 238000006073 displacement reaction Methods 0.000 claims description 11
- 238000009826 distribution Methods 0.000 claims description 5
- 238000000034 method Methods 0.000 claims description 3
- 239000012530 fluid Substances 0.000 claims 3
- 230000001427 coherent effect Effects 0.000 claims 1
- 230000007423 decrease Effects 0.000 claims 1
- 239000007795 chemical reaction product Substances 0.000 abstract description 4
- 239000000446 fuel Substances 0.000 abstract description 4
- 238000004140 cleaning Methods 0.000 abstract description 2
- 230000003068 static effect Effects 0.000 abstract description 2
- 239000002912 waste gas Substances 0.000 abstract description 2
- 230000000712 assembly Effects 0.000 abstract 1
- 238000000429 assembly Methods 0.000 abstract 1
- 238000000354 decomposition reaction Methods 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- 230000001143 conditioned effect Effects 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 239000002480 mineral oil Substances 0.000 description 2
- 235000010446 mineral oil Nutrition 0.000 description 2
- 230000000717 retained effect Effects 0.000 description 2
- LFQSCWFLJHTTHZ-UHFFFAOYSA-N Ethanol Chemical compound CCO LFQSCWFLJHTTHZ-UHFFFAOYSA-N 0.000 description 1
- 239000003225 biodiesel Substances 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
- F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
- F04B17/046—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the fluid flowing through the moving part of the motor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/02—Lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/02—Lubrication
- F04B39/0223—Lubrication characterised by the compressor type
- F04B39/0276—Lubrication characterised by the compressor type the pump being of the reciprocating piston type, e.g. oscillating, free-piston compressors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/06—Cooling; Heating; Prevention of freezing
Abstract
Object is the bearing that the reciprocating plunger pump (1) making to be driven by electromagnet (2) has plunger (2) in cylinder body (10), protects this bearing to avoid local superheating and prevents bearing from decomposing, and discharges the wear debris of reaction product and any generation.For this purpose, the recess elongated is arranged in a bearing surface in two bearing surfaces in the bearing play (11) between plunger (9) and cylinder body (10), the liquid stream of being carried by plunger (9) flows through this recess in whole or in part, and plunger (9) interacts in order to the transporting velocity of reciprocating plunger pump and other assemblies of reciprocating plunger pump.The reciprocating plunger pump of described type is used as metering pump in the static heater of the fuel handling in vehicle, auxiliary heater and waste gas cleaning system and transfer pump.
Description
Technical field
The present invention relates to a kind of reciprocating plunger pump by solenoid actuated, corresponding to the preamble of claim 1.
Background technique
By solenoid actuated and for carrying and being quantitatively such as well-known from DE4328621 and DE102001111926 to the reciprocating plunger pump of fuel, and tried out and tested.
Along with having not based on mineral oil, relatively high a part of content of such as such as biodiesel or alcohol, and therefore also there is the popularization of the fuel of relatively high a part of water, the material of friction partner, especially the material of plunger and the material of cylinder body just must be adjusted; But, in certain operational situations, in this metering pump, still can run into new wear phenomenon.If wear phenomenon is such as lost efficacy by the lubricating film of local restricted to occur and the local superheating that produces causes, or cause by the greasy property only based on the relevant reduction of the medium of mineral oil.
Can know from document US2337821 and US3153897, on circumferencial direction and longitudinal direction both direction, continuous print groove is arranged on plunger surface, this groove be applicable to strengthen lubrication and, if properly, be applicable to wear debris to be retained in groove.Groove passing hole is partly connected to the active side of pump plunger.Document US2231861, US2371848 and US5140905 it is also proposed the pump with axial circumferential groove, and liquid is transported to pump via hole.
Document US2937659 proposes to be had safety check and is accommodated in pump plunger wherein, and wherein, the volume flow be transferred is discharged on the pressure side via the groove in plunger by safety check.
Document 4644851 proposes wherein that Plunger bearing is by pressure field by the compressor of assisting, and wherein, medium is transported to pressure field from the active side of plunger.
Summary of the invention
A target of the present invention guides liquid stream through the bearing play plunger and cylinder body, and wherein, liquid stream cooling bearing also discharges the potential wear debris of any decomposition and reaction product and generation.Here, the quantitative validity of reciprocating plunger pump should be maintained, and cost of production should significantly not increase.
This target is implemented by means of the feature describing claim 1, and wherein, dependent claims illustrate in greater detail solution.
By the reciprocating plunger pump of solenoid actuated except required port, two valves and case member, also comprise plunger, this plunger to be contained in cylinder body and to support electromagnet armature plunger with being closed.In order to realize not relying on the conveying of pressure and quantitatively accurate, bearing just at least must show minimum bearing play in a part, and described bearing must adapt to the transverse force of armature piston, wherein, when electromagnet is energized, the bearing part of armature chamber side bears its maximum load.
Potential wear debris in order to cooling bearing and in order to discharge decomposition and reaction product and generation, the such as spiral shaped recess of the length of spiral slot or shallow screw thread is arranged at least one surface in two surfaces in the bearing play between plunger and cylinder body.Liquid stream flows through described recess, in during shifting process, this liquid stream is under any circumstance all carried by the plunger of reciprocating plunger pump, this is because for this purpose and arrange conduction pipe, the transverse holes preferably in plunger makes the safety check being arranged in plunger be connected with recess.Have from displacement room to armature chamber conveying and have the first embodiment of the reciprocating plunger pump of two safety check, the liquid stream of reciprocating plunger pump via the transverse holes in plunger from one of safety check by the recess all guided to the surface of plunger or cylinder body, and be directed in armature chamber via the bearing region of armature chamber side, wherein, recess extends in armature chamber.Here, the transporting velocity of reciprocating plunger pump is unaffected or be only subject to minimum impact, this is because between transverse holes and displacement body chamber, plunger opposing cylinder seals.But shortcoming is that the contact in the bearing region of the armature chamber side of cylinder body increases.
In a second embodiment, contrary with the first embodiment, only the liquid stream of a part of pump is directed via transverse holes, and the liquid stream of remainder directly enters armature chamber through plunger and another transverse holes, and wherein, the size of transverse holes determines the distribution of shunting.
In the third embodiment, the liquid stream of reciprocating plunger pump via the first transverse holes in plunger from safety check by the recess all guided to the surface of plunger or cylinder body, then get back to via the second transverse holes in the second longitudinal hole in plunger, and then enter in armature chamber via the 3rd transverse holes.Here, described recess does not extend in armature chamber.Like this, the bearing region of the high loading adjoined with armature chamber can be formed and not have recess.
Also be such situation in the present embodiment, namely the transporting velocity of reciprocating plunger pump is unaffected or be only subject to the through-flow minimum impact of bearing.The shortcoming of the present embodiment is through the pressure drop of transverse holes, this is because the liquid stream of reciprocating plunger pump has to pass through three transverse holes.
In the fourth embodiment, in the variation of the 3rd embodiment, part pump liquid is only had to flow through by bearing region directed, and the liquid stream of remainder is directed into the second longitudinal hole via throttling joint from the first longitudinal hole, wherein, first transverse holes size and secondly throttling joint determine the distribution of shunting.
Third and fourth embodiment may be modified as liquid stream via the transverse holes in cylinder body and is directed to armature chamber via the bearing region that other conduction pipe flows through from stream.Corresponding to the second embodiment, shunting can be directed to armature chamber via the transverse holes in plunger, and wherein, again, the size of described transverse holes determines the distribution of shunting.
Embodiment as above relates to and liquid stream is guided to displacement body chamber from entrance and then guides to the reciprocating plunger pump of outlet via armature chamber.But technology of the present invention instruction can also be applied to liquid stream being guided in armature chamber from entrance and then guiding to the reciprocating plunger pump of outlet via displacement body chamber.Which results in the different direction of the liquid stream through bearing, but all essential characteristics of the present invention are retained.
Described embodiment is applicable to cool the bearing play between plunger and cylinder body, and if properly, discharge again the potential wear debris of decomposition and reaction product and generation in addition.Third and fourth embodiment has not by bearing region that recess interrupts at the armature chamber side of cylinder body.First and second embodiments are that the liquid that will be transferred provides low pressure effective impedance.
In order to the operation of reciprocating plunger pump, to the electric current that electromagnet uses controlled voltage or is conditioned.Power supply has the timing chart about the time, and wherein, frequency determines the transporting velocity of reciprocating plunger pump, and dutycycle is consistent with at the pressure at delivery side of pump place, and the side gradient of pulse is consistent with the demand of the liquid stream through cylinder body.Here, steep side gradient can help the Rapid Variable Design realized in liquid stream, and this is conducive to discharging wear debris from bearing region.For this purpose, adapt to require and side gradient in order to adjust regulation in order to make current power supply, the fundamental frequency of pulse power supply is the additional pulse duration modulation of superposition thereon.By means of being generated by the target that the manipulation of the side gradient of the pulse duration modulation of superposition also can be referred to as applicable harmonic wave of describing.
The reciprocating plunger pump of described type is used as metering pump in the static heater of the fuel handling in vehicle, auxiliary heater and waste gas cleaning system and transfer pump.
Accompanying drawing explanation
Fig. 1 shows the metering pump according to prior art.
Fig. 2 shows the reciprocating plunger pump with the transverse holes of close valve of the first or second embodiment.
Fig. 3 shows the reciprocating plunger pump in plunger with three transverse holes of the 3rd or the 4th embodiment.
Fig. 4 shows the reciprocating plunger pump in cylinder body with transverse holes.
Fig. 5 shows the oscillogram of the voltage and current for characteristic startup of the manipulation by side gradient.
Symbol description
1 ... reciprocating plunger pump
2 ... electromagnet
3 ... first displacement body chamber
4 ... armature chamber
5 ... first safety check
6 ... second valve
7 ... entrance
8 ... outlet
9 ... plunger
10 ... cylinder body
11 ... bearing play
12 ... armature piston
13 ... first transverse holes
14 ... second transverse holes
15 ... longitudinal hole
16 ... 3rd transverse holes
17 ... second longitudinal hole
21 ... clutch shaft bearing region
22 ... second bearing region
23 ... 3rd bearing region
29 ... hole
30 ... transverse holes
31 ... conduction pipe
Embodiment
The reciprocating plunger pump 1 driven by electromagnet 2 comprises two safety check 5 and 6, and comprises plunger 9, and plunger 9 to be contained in cylinder body 10 and to support the armature piston of electromagnet 2 with being closed.
The recess that Fig. 2 shows elongation is arranged in a surface in two surfaces of the bearing play 11 between plunger 9 and cylinder body 10, and the liquid stream be transferred flows through this recess.For this purpose, transverse holes 13 creates the connection from valve 6 to bearing play 11.
According in first and second embodiments of Fig. 2, the liquid stream of reciprocating plunger pump 1 via transverse holes 13 from valve 6 by the recess guided in whole or in part the surface of plunger 9 or in the surface of cylinder body 10, and being directed in armature chamber 4 via bearing region 22 and 23, its center dant extends in armature chamber 4 and does not extend in displacement room 3.
Second embodiment is different from the first embodiment is that only some liquid stream is directed via bearing play 11, and wherein, the remaining partial amount of liquid stream is directed in armature chamber 4 via transverse holes 16.
According in third and fourth embodiment of Fig. 3, the liquid stream of reciprocating plunger pump 1 via transverse holes 13 from valve 6 by the recess guided in whole or in part the surface of plunger 9 or in the surface of cylinder body 10, then be directed in the longitudinal hole 17 of plunger via transverse holes 14, and be then directed in armature chamber 4 via transverse holes 16.Recess not to extend in armature chamber and does not extend in displacement body chamber 3.
In the fourth embodiment, by contrasting with the 3rd embodiment, the liquid stream of reciprocating plunger pump is only partly guided via bearing region 22, this is because the partial amount of liquid stream flows out from longitudinal hole 15 and flows in the second longitudinal hole 17 via hole 29.
According to Fig. 4, the third and fourth embodiment may be modified as liquid stream via the transverse holes 30 in cylinder body and the bearing region 22 flow through from stream via conduction pipe 31 is further directed to armature chamber.Corresponding to the second embodiment, shunting can be directed to armature chamber via the transverse holes 16 in plunger, and wherein, the size of described transverse holes determines the distribution of shunting.
During operation, for the controlled voltage supplied to electromagnet 2 or the electric current be conditioned, there is the timing chart about the time, as shown in Figure 5.In order to reduce power supply as requested and handle harmonic content and the side gradient of pulse, described timing chart may the additional pulse duration modulation of superposition thereon.Here, fundamental frequency determines the transporting velocity of reciprocating plunger pump, and the dutycycle be associated is consistent with the pressure in the outlet port at reciprocating plunger pump, and the side gradient of pulse is consistent with the demand of the liquid stream via cylinder body.
Claims (9)
1. the reciprocating plunger pump (1) of an Electromagnetic Drive, the reciprocating plunger pump (1) of described Electromagnetic Drive has plunger (9), described plunger (9) makes liquid stream be shifted and supports the armature piston (12) of electromagnet (2), and for this purpose, described plunger (9) is contained in cylinder body (10) with being closed
It is characterized in that:
More than one recess is arranged at least one surface in two surfaces in the bearing play (11) between described plunger (9) and described cylinder body (10), wherein, each recess continues in the quite most length of described plunger (9) or described cylinder body (10), and wherein, in order to cover most surfaces, described recess has spiral shape, and wherein, described recess is connected with valve (6) via low resistance fluid joint, and be connected with armature chamber (4) via other low resistance fluid joint, and the liquid stream of being carried by described plunger (9) flows through described recess in whole or in part, described plunger (9) interacts in order to the output rating of described reciprocating plunger pump and described cylinder body (10).
2. reciprocating plunger pump as claimed in claim 1, it is characterized in that, described low resistance fluid joint is the first transverse holes (13).
3. reciprocating plunger pump as claimed in claim 2, it is characterized in that, the liquid stream of described reciprocating plunger pump (1) via described first transverse holes (13) by the described recess all guided in the surface of described plunger (9) or described cylinder body (10), and be directed in the described armature chamber (4) that adjoins with bearing via bearing region (22 and 23), wherein, described recess extends in described armature chamber (4) and does not extend in displacement body chamber (3).
4. reciprocating plunger pump as claimed in claim 2, it is characterized in that, the liquid stream of described reciprocating plunger pump (1) via described first transverse holes (13) by the described recess partly guided in the surface of described plunger (9) or described cylinder body (10), and be directed in the described armature chamber (4) that adjoins with bearing via bearing region (22 and 23), wherein, described recess extends in described armature chamber (4) and does not extend in displacement body chamber (3), wherein, another part amount of the described liquid stream of described reciprocating plunger pump is directed in described armature chamber (4) via the 3rd other transverse holes (16).
5. reciprocating plunger pump as claimed in claim 2, it is characterized in that, the liquid stream of described reciprocating plunger pump (1) via described first transverse holes (13) by the described recess all guided in the surface of described plunger (9) or described cylinder body (10), then be directed in the second longitudinal hole (17) in described plunger via the second transverse holes (14), and be then directed in described armature chamber (4) via the 3rd transverse holes (16), wherein, described recess not to extend in described armature chamber (4) and does not extend in displacement body chamber (3).
6. reciprocating plunger pump as claimed in claim 2, it is characterized in that, the liquid stream of described reciprocating plunger pump (1) via described first transverse holes (13) by the described recess partly guided in the surface of described plunger (9) or described cylinder body (10), then be directed in the second longitudinal hole (17) in described plunger via the second transverse holes (14), and be then directed in described armature chamber (4) via the 3rd transverse holes (16), wherein, another part amount of the described liquid stream of described reciprocating plunger pump is directed in described second longitudinal hole (17) via hole (29) from the first longitudinal hole (15), and wherein, described recess not to extend in described armature chamber (4) and does not extend in displacement body chamber (3).
7. reciprocating plunger pump as claimed in claim 2, it is characterized in that, the liquid stream of described reciprocating plunger pump (1) is directed to the described recess in the surface of described plunger (9) or described cylinder body (10) via described first transverse holes (13), is then directed to described armature chamber via conduction pipe (31) further via the transverse holes (30) in cylinder body.
8. reciprocating plunger pump as claimed in claim 2, it is characterized in that, the liquid stream of described reciprocating plunger pump (1) via described first transverse holes (13) by the described recess partly guided in the surface of described plunger (9) or described cylinder body (10), then described armature chamber is directed to via conduction pipe (31) further via the transverse holes (30) in cylinder body, wherein, another part amount of the described liquid stream of described reciprocating plunger pump is directed in described armature chamber (4) via the 3rd transverse holes (16) from the first longitudinal hole (15), and wherein, the size of described transverse holes determines the distribution of shunting.
9. one kind for operating the method for reciprocating plunger pump as claimed in claim 1, it is characterized in that, voltage or electric current for being supplied to electromagnet (2) have the timing chart of the repetition about the time, described timing chart presents incoherence in the mode of pulse duration modulation, wherein, fundamental frequency determines transporting velocity, relevant dutycycle is consistent with at the pressure at delivery side of pump place, and the uplifted side of coherent pulse is consistent with the demand of the liquid stream via the bearing in cylinder body with the side gradient of decline side.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102012006782.8 | 2012-04-03 | ||
| DE102012006782.8A DE102012006782B4 (en) | 2012-04-03 | 2012-04-03 | Electromagnetically driven reciprocating pump with a through the pump fluid perfused sliding bearing with recesses in the region of the bearing gap between the piston and cylinder |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103362771A CN103362771A (en) | 2013-10-23 |
| CN103362771B true CN103362771B (en) | 2015-12-02 |
Family
ID=49209703
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310113844.2A Expired - Fee Related CN103362771B (en) | 2012-04-03 | 2013-04-02 | There is the reciprocating plunger pump of the sliding bearing that stream flows through |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US9394890B2 (en) |
| CN (1) | CN103362771B (en) |
| DE (1) | DE102012006782B4 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105756881B (en) * | 2014-12-16 | 2018-11-06 | 天纳克（苏州）排放系统有限公司 | Plunger pump with position limiting structure and its application |
| CN109386447A (en) * | 2017-08-08 | 2019-02-26 | 三花亚威科电器设备（芜湖）有限公司 | Electromagnetic pump |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4644851A (en) * | 1984-02-03 | 1987-02-24 | Helix Technology Corporation | Linear motor compressor with clearance seals and gas bearings |
| DE4328621A1 (en) * | 1993-08-26 | 1995-03-02 | Thomas Magnete Gmbh | Electromagnetically drivable pump, in particular a metering pump (proportioning pump) |
| CN1146533A (en) * | 1995-08-21 | 1997-04-02 | Lg电子株式会社 | Noise-reducing device for linear compressor |
| JP2003021051A (en) * | 2001-07-09 | 2003-01-24 | Nippon Control Kogyo Co Ltd | Electromagnetic pump |
| CN2632336Y (en) * | 2003-06-05 | 2004-08-11 | 顾丰乐 | Electromagnetic pumps |
| DE102010019821A1 (en) * | 2010-05-08 | 2011-11-10 | Thomas Magnete Gmbh | Reciprocating piston pump for e.g. dosing fuel for auxiliary heating system in motor vehicle, has membrane dimensioned with respect to outer diameter, thickness and support such that membrane does not completely rest against magnetic coil |
Family Cites Families (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1396296A (en) | 1919-03-21 | 1921-11-08 | William J Springer | Pump |
| US1425191A (en) | 1919-12-26 | 1922-08-08 | Garbarini Andre | Pumping apparatus |
| US2231861A (en) | 1938-09-27 | 1941-02-18 | Edward E Adams | Well pump |
| US2371848A (en) | 1942-02-10 | 1945-03-20 | Phillips Petroleum Co | Process for the production of butadiene |
| US2337821A (en) | 1942-12-02 | 1943-12-28 | Hydraulic Controls Inc | Pump |
| US2371846A (en) | 1943-03-26 | 1945-03-20 | Ruthven Side Pocket Dam Corp | Pump |
| US2937659A (en) | 1958-01-09 | 1960-05-24 | Dresser Ind | Ball valve cage |
| US2953993A (en) * | 1958-02-12 | 1960-09-27 | Strickland Gerald | Pump construction |
| US3153987A (en) | 1960-06-29 | 1964-10-27 | Thoma Hans | Piston type hydrostatic power units |
| US3153897A (en) | 1961-12-26 | 1964-10-27 | Richard A Kummerer | Chain |
| FR1407722A (en) | 1964-06-22 | 1965-08-06 | Commissariat Energie Atomique | Electromagnetic pump |
| DE1301956B (en) | 1966-04-02 | 1969-08-28 | Eberspaecher J | Fuel piston pump |
| US4169695A (en) | 1976-08-20 | 1979-10-02 | Jidosha Kiki Co., Ltd. | Electromagnetic pump with pressure-regulating mechanism |
| JPS5416703A (en) | 1977-07-08 | 1979-02-07 | Taisan Kougiyou Kk | Boosting delay apparatus for solenoid plunger pump and so on |
| DE3504789A1 (en) | 1985-02-13 | 1986-08-14 | Webasto-Werk W. Baier GmbH & Co, 8035 Gauting | ELECTROMAGNETICALLY ACTUATED PISTON PUMP |
| US5140905A (en) | 1990-11-30 | 1992-08-25 | Mechanical Technology Incorporated | Stabilizing gas bearing in free piston machines |
| JPH0642372A (en) * | 1992-07-23 | 1994-02-15 | Zexel Corp | Fuel injection control device |
| JP2002039057A (en) | 2000-07-28 | 2002-02-06 | Silver Kk | Electromagnetic pump |
| US7607422B2 (en) * | 2005-04-25 | 2009-10-27 | Grant B Carlson | Methods of flexible fuel engine conversions |
| DE102011111926A1 (en) | 2011-08-31 | 2013-02-28 | Thomas Magnete Gmbh | Electromotive pump |
-
2012
- 2012-04-03 DE DE102012006782.8A patent/DE102012006782B4/en not_active Expired - Fee Related
-
2013
- 2013-03-27 US US13/851,282 patent/US9394890B2/en active Active
- 2013-04-02 CN CN201310113844.2A patent/CN103362771B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4644851A (en) * | 1984-02-03 | 1987-02-24 | Helix Technology Corporation | Linear motor compressor with clearance seals and gas bearings |
| DE4328621A1 (en) * | 1993-08-26 | 1995-03-02 | Thomas Magnete Gmbh | Electromagnetically drivable pump, in particular a metering pump (proportioning pump) |
| CN1146533A (en) * | 1995-08-21 | 1997-04-02 | Lg电子株式会社 | Noise-reducing device for linear compressor |
| JP2003021051A (en) * | 2001-07-09 | 2003-01-24 | Nippon Control Kogyo Co Ltd | Electromagnetic pump |
| CN2632336Y (en) * | 2003-06-05 | 2004-08-11 | 顾丰乐 | Electromagnetic pumps |
| DE102010019821A1 (en) * | 2010-05-08 | 2011-11-10 | Thomas Magnete Gmbh | Reciprocating piston pump for e.g. dosing fuel for auxiliary heating system in motor vehicle, has membrane dimensioned with respect to outer diameter, thickness and support such that membrane does not completely rest against magnetic coil |
Also Published As
| Publication number | Publication date |
|---|---|
| US9394890B2 (en) | 2016-07-19 |
| DE102012006782A1 (en) | 2013-10-10 |
| CN103362771A (en) | 2013-10-23 |
| DE102012006782B4 (en) | 2018-08-09 |
| US20130280103A1 (en) | 2013-10-24 |
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